JP2013147975A - Valve timing adjusting device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve timing adjusting device configured to reduce abnormal noise and improve responsiveness.SOLUTION: A driving rotor 11 includes a first sun gear part 123, and rotates along with a crankshaft. A follower rotor 14 includes a second sun gear part 143, and rotates along with a camshaft 4. A planetary rotor 15 includes a first planetary gear part 154, a second planetary gear part 155, and a shaft hole 153, and changes a relative rotational phase between the driving rotor 11 and the follower rotor 14. A cylindrical shaft 16 has a biasing part 17, is set in the shaft hole 153 so as to be rotated relatively with the planetary rotor 15, and supports the planetary rotor 15 rotatably. The biasing part 17 biases the planetary rotor 15 toward a meshing side of the first planetary gear part 154 with the second planetary gear part 155 and a meshing side of the first sun gear part 123 with the second sun gear part 143, where the biasing force increases as a temperature increases, and decreases as the temperature decreases.

Description

  The present invention relates to a valve timing adjusting device.

  2. Description of the Related Art Conventionally, there is known a valve timing adjusting device that adjusts a valve timing by changing a relative rotational phase between two rotating bodies that rotate in conjunction with a crankshaft and a camshaft. For example, Patent Document 1 includes a planetary rotator housed in a space composed of a drive rotator and a driven rotator, and a planet carrier that rotatably supports the planetary rotator. A valve timing adjusting device that changes the relative rotational phase of a driving rotating body and a driven rotating body is disclosed.

  In the valve timing adjusting device described in Patent Document 1, an elastic member is provided on the outer side in the radial direction of the planet carrier, and the planetary rotator is biased toward the meshing side of the planetary rotator, the drive rotator, and the driven rotator. . This suppresses abnormal noise caused by meshing of the drive-side external gear portion and the driven-side external gear portion of the planetary rotating body with the drive-side internal gear portion of the drive-rotating body and the driven-side internal gear portion of the driven-rotating body. I am trying.

JP 2010-159706 A

By the way, in the valve timing adjusting device described in Patent Document 1, lubricating oil is supplied between the planetary rotating body, the driving rotating body, and the driven rotating body.
The viscosity of the lubricating oil changes as the temperature changes. When the temperature is high, the viscosity of the lubricating oil becomes low, so that abnormal noise generated between the planetary rotator, the driving rotator, and the driven rotator tends to occur. In addition, since the viscosity of the lubricating oil increases at low temperatures, the responsiveness of the planetary rotator driven and rotated by the motor decreases.

  Here, it is considered that the generation of abnormal noise at high temperatures can be suppressed by increasing the biasing force of the elastic member, but the problem that the responsiveness decreases at low temperatures cannot be solved.

In addition, it is considered that by reducing the biasing force of the elastic member, it is possible to suppress a decrease in responsiveness at low temperatures, but the problem of abnormal noise occurring at high temperatures cannot be solved.
The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a valve timing adjusting device capable of both suppressing abnormal noise and improving responsiveness.

  According to the first aspect of the present invention, the valve timing adjusting device is provided in the driving force transmission system that transmits the driving force of the internal combustion engine from the driving shaft to the driven shaft, and is at least of an intake valve and an exhaust valve that are driven to open and close by the driven shaft. One of the opening / closing timings is adjusted. The valve timing adjusting device includes a first rotating body, a second rotating body, a planetary rotating body, a cylindrical shaft, and an urging unit. The first rotating body is formed in a cylindrical shape, has a first sun gear portion inside, and rotates in conjunction with one of the drive shaft and the driven shaft. The second rotating body is formed in a cylindrical shape, has a second sun gear portion having an inner diameter different from that of the first sun gear portion, and rotates in conjunction with the other of the drive shaft and the driven shaft. The planetary rotator has a first planetary gear portion that meshes with the first sun gear portion, a second planetary gear portion that meshes with the second sun gear portion, and a shaft hole. And the relative rotational phase of the second rotating body are changed. The cylindrical shaft has an urging portion, is provided in the shaft hole so as to be rotatable relative to the planetary rotator, and rotatably supports the planetary rotator. The urging unit urges the planetary rotating body toward the meshing side of the first planetary gear unit and the second planetary gear unit and the first sun gear unit and the second sun gear unit, and the urging force increases as the temperature increases. The urging force decreases as the temperature decreases.

  In the present invention, the urging force of the urging unit increases as the temperature increases, and the urging force decreases as the temperature decreases. As a result, the urging unit urges the planetary rotator toward the meshing side of the first planetary gear unit and the second planetary gear unit, the first sun gear unit, and the second sun gear unit with a high urging force at high temperatures. . Therefore, when the viscosity of the lubricating oil decreases due to a high temperature, it is possible to suppress abnormal noise generated by the engagement of the first sun gear and the second sun gear with the first planetary gear and the second planetary gear.

  On the other hand, the urging unit urges the planetary rotator toward the meshing side of the first planetary gear unit and the second planetary gear unit, the first sun gear unit, and the second sun gear unit with a low urging force at low temperatures. Therefore, when the viscosity of the lubricating oil increases due to low temperature, the friction torque between the planetary rotating body and the first and second rotating bodies can be reduced, and the planetary rotating body driven and rotated by the motor can be reduced. Responsiveness can be improved.

Sectional drawing of the valve timing adjustment apparatus by 1st Embodiment of this invention. The schematic diagram of the driving force transmission system by 1st Embodiment of this invention. III-III sectional view taken on the line of FIG. The IV section enlarged view of FIG. Sectional drawing of the valve timing adjustment apparatus by 2nd Embodiment of this invention. The VI section enlarged view of FIG.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
A valve timing adjusting apparatus according to a first embodiment of the present invention is shown in FIGS. The valve timing adjusting device 10 of this embodiment is a motor-driven valve timing adjusting device driven by a motor 21. In the driving force transmission system provided in the valve timing adjusting device 10 of the present embodiment, as shown in FIG. 2, a gear fixed to a crankshaft 2 as a driving shaft of an internal combustion engine (hereinafter referred to as “engine”) 1. 3 and the sprocket gears 134 and 6 fixed to the camshafts 4 and 5 as driven shafts are wound around the timing chain 7, and the driving force is transmitted from the crankshaft 2 to the camshafts 4 and 5. The camshaft 4 drives the intake valve 8 to open / close via the cam mechanism, and the camshaft 5 drives the exhaust valve 9 to open / close via the cam mechanism. The valve timing adjusting device 10 according to the present embodiment adjusts the rotational phase between the drive rotor 11 that rotates in conjunction with the crankshaft 2 and the driven rotor 14 that rotates in conjunction with the camshaft 4. Then, the opening / closing timing of the intake valve 8 is adjusted.

  As shown in FIG. 1, the valve timing adjusting device 10 includes a drive rotator 11 as a first rotator, a driven rotator 14 as a second rotator, a planetary rotator 15, a cylindrical shaft 16, and an urging unit 17. Is provided.

  The drive rotator 11 and the driven rotator 14 have an internal space 110 that accommodates the planetary rotator 15, the cylindrical shaft 16, and the biasing portion 17. Lubricating oil is supplied into the accommodation space 110 by the pump 100 via the supply passage 41.

  The drive rotating body 11 is configured by coaxially combining a bottomed cylindrical drive gear member 12 and a two-stage cylindrical sprocket 13. Hereinafter, in the valve timing adjusting device 10, the drive gear member 12 side is referred to as “one end side”, and the sprocket 13 side is referred to as “other end side”. In the cylindrical member, a radially inner wall surface is referred to as an “inner wall”, and a radially outer wall surface is referred to as an “outer wall”. The drive gear member 12 and the sprocket 13 are fastened by screws 111.

  The drive gear member 12 has a drive cylinder 121 and a drive bottom 122. A first sun gear portion 123 is formed on the inner wall of the drive cylinder portion 121 with the tooth tip circular surface on the inner peripheral side of the root circle. A central hole 124 that penetrates the drive bottom 122 in the axial direction is formed in the center of the drive bottom 122.

  The sprocket 13 has a large diameter part 131, a small diameter part 132, and a step part 133. Here, the drive gear member 12 is screwed to the sprocket 13 with the outer wall of the drive cylinder 121 fitted to the inner wall of the large-diameter portion 131 of the sprocket 13. The sprocket 13 has a sprocket gear 134 that protrudes radially outward of the outer wall of the stepped portion 133. The sprocket 13 is connected to the crankshaft 2 by the timing chain 7 that is stretched around the sprocket gear 134. Therefore, the drive rotator 11 rotates in conjunction with the crankshaft 2.

  The driven rotator 14 is provided coaxially with the drive rotator 11 and the camshaft 4. The driven rotor 14 is formed in a bottomed cylindrical shape, and has a driven cylinder portion 141 and a driven bottom portion 142.

  The driven bottom 142 is bolted to the end of one end of the camshaft 4. By this bolt fixing, the driven rotating body 14 is integrated with the camshaft 4 and can rotate about the central axis O <b> 1 of the camshaft 4 together with the camshaft 4. The driven rotator 14 is rotatable relative to the drive rotator 11. Here, the relative rotation direction in which the driven rotator 14 is advanced with respect to the drive rotator 11 is referred to as an advance angle X, and the relative rotation direction in which the driven rotator 14 is retarded with respect to the drive rotator 11 is retarded. It is referred to as direction Y (see FIG. 3).

  On the inner wall of the driven cylinder portion 141, a second sun gear portion 143 is formed with a tooth tip circle surface on the inner peripheral side of the root circle. Here, the root circle of the second sun gear portion 143 is formed to have a smaller diameter than the root circle of the first sun gear portion 123. The number of teeth of the second sun gear portion 143 is set to be smaller than the number of teeth of the first sun gear portion 123.

  The outer wall of the driven cylinder part 141 is fitted to the inner wall of the small diameter part 132 and the step part 133 in the sprocket 13, and the driven rotary body 14 supports the drive rotary body 11 so as to be relatively rotatable.

  The planetary rotator 15 is formed in a two-stage cylindrical shape, and includes a first cylinder part 151, a second cylinder part 152, and a shaft hole 153. The outer diameter of the first cylinder part 151 is formed larger than the outer diameter of the second cylinder part 152. The planetary rotator 15 is provided such that the first cylinder portion 151 is located inside the drive cylinder portion 121 and the second cylinder portion 152 is located inside the driven cylinder portion 141.

  A first planetary gear portion 154 is formed on the outer wall of the first cylindrical portion 151, with the tip circle on the outer peripheral side of the root circle. The number of teeth of the first planetary gear portion 154 is set to be a predetermined number less than the number of teeth of the first sun gear portion 123. A part of the first planetary gear part 154 meshes with a part of the first sun gear part 123.

A second planetary gear portion 155 is formed on the outer wall of the second cylindrical portion 152. The second planetary gear portion 155 has a tip circle on the outer peripheral side of the root circle. The root circle of the second planetary gear portion 155 has a smaller diameter than the root circle of the first planetary gear portion 154. The number of teeth of the second planetary gear portion 155 is set to be a predetermined number less than the number of teeth of the second sun gear portion 143. A part of the second planetary gear part 155 meshes with a part of the second sun gear part 143.
The shaft hole 153 is formed at the center of the second cylinder part 152 and penetrates the second cylinder part 152 in the axial direction.

  The cylindrical shaft 16 is formed in a cylindrical shape, and includes an input portion 161 formed on one end side in the axial direction, an eccentric portion 162 formed on the other end side, and an urging portion 17.

  The input portion 161 has a cylindrical wall with a uniform thickness, and has a cylindrical shape that is coaxial with the drive rotator 11, the driven rotator 14, the camshaft 4, and the motor shaft 212. A joint 163 that fixes the motor shaft 212 is formed inside the input unit 161. Further, the input portion 161 is disposed on the radially inner side of the central hole 124 of the drive gear member 12 and supports the drive rotator 11 via the bearing 18 so as to be rotatable.

  The eccentric part 162 is formed in a cylindrical shape, and has an eccentric cylindrical shape in which the center of the outer wall and the center of the inner wall are different. Here, the center of the outer wall is defined as a central axis O2. The eccentric portion 162 is provided such that the center of the inner wall is coaxial with the centers of the drive rotator 11, the driven rotator 14, the camshaft 4, and the motor shaft 212. Moreover, the eccentric part 162 is formed so that the radial thickness of the peripheral wall differs in the circumferential direction. Here, a portion where the radial thickness is formed thicker than the average thickness is referred to as a thick portion 164, and a portion where the radial thickness is formed thinner than the average thickness is referred to as a thin portion 165. The eccentric portion 162 is disposed on the radially inner side of the shaft hole 153 and supports the planetary rotating body 15 via the bearing 19 so as to be rotatable.

  Here, when the cylindrical shaft 16 rotates around the central axis O1 by the rotation of the motor shaft 212, the planetary rotator 15 rotates around the central axis O2 while revolving around the central axis O1. Then, on the thick part 164 side, a part of the first sun gear part 123 and a part of the first planetary gear part 154 are engaged, and a part of the second sun gear part 143 and one of the second planetary gear parts 155 are engaged. The part meshes.

  As shown in FIG. 3, two urging portions 17 are provided on the outer wall of the thick portion 164 of the eccentric portion 162. Further, the two urging portions 17 are respectively provided on both sides in the circumferential direction of the thick portion 164 where the thickest portion 164 is formed thickest in the radial direction of the eccentric portion 162.

  The urging portion 17 includes an accommodation recess 171 formed on the outer wall of the eccentric portion 162 and an urging member 172 accommodated in the accommodation recess 171. The housing recess 171 is a recess that is recessed a predetermined distance radially inward from the outer wall of the eccentric portion 162, and has a bottom portion 175. Here, the bottom portion 175 of the housing recess 171 corresponds to a “seat surface portion” in the claims.

  The urging member 172 is a metal leaf spring having a substantially U-shaped cross section perpendicular to the axial direction of the cylindrical shaft 16. The urging member 172 is supported by the bottom portion 175, and is engaged with the first planetary gear portion 154 and the second planetary gear portion 155, the first sun gear portion 123 and the second sun gear portion 143 via the bearing 19 ( Hereinafter, the planetary rotator 15 is urged toward the “meshing side”. In the present embodiment, the urging member 172 includes a high expansion layer 173 and a low expansion layer 174 in the plate thickness direction. The high expansion layer 173 and the low expansion layer 174 are formed of two different types of metals. The high expansion layer 173 is, for example, an alloy containing nickel, iron, and chromium, and has a predetermined coefficient of thermal expansion. The low expansion layer 174 is, for example, an alloy containing nickel and iron, and has a thermal expansion coefficient lower than that of the high expansion layer 173. That is, the urging member 172 is made of bimetal. The high expansion layer 173 is formed on the inner side, and the low expansion layer 174 is formed on the outer side. Therefore, the urging force of the urging member 172 toward the meshing side increases as the temperature increases, and decreases as the temperature decreases.

  The control unit 20 includes a motor 21 and a control unit 22. The motor 21 is disposed on the opposite side of the camshaft 4 with the valve timing adjusting device 10 interposed therebetween. The motor 21 is, for example, a brushless motor or the like, and includes a motor case 211 fixed to the engine 1 and a motor shaft 212 supported by the motor case 211 so as to be rotatable forward and backward. The control unit 22 is an electric circuit such as a microcomputer, and is disposed outside the motor case 211 and is electrically connected to the motor 21. The control unit 22 controls energization of the motor 21 according to the operating state of the internal combustion engine. By this energization control, the motor 21 forms a rotating magnetic field around the motor shaft 212, and outputs rotational torque in the directions X and Y (see FIG. 3) corresponding to the direction of the rotating magnetic field from the motor shaft 212.

Next, the operation of the valve timing adjusting device 10 will be described.
In the present embodiment, the drive rotator 11 and the driven rotator 14 are engaged with the first sun gear portion 123 and the first planetary gear portion 154, and between the second sun gear portion 143 and the second planetary gear portion 155. It is linked via the planetary rotor 15 by meshing.

  When the cylindrical shaft 16 does not rotate relative to the drive rotator 11, the planetary rotator 15 has a meshing position between the first planetary gear portion 154 and the first sun gear portion 123, and the second planetary gear portion 155 and the first planetary gear portion 155. 2 Rotates with the drive rotator 11 and the driven rotator 14 while maintaining the meshing position with the sun gear 143. Thereby, since the relative rotational phase between the drive rotator 11 and the driven rotator 14 is maintained, the valve timing is also maintained.

  On the other hand, when the cylindrical shaft 16 relatively rotates in the advance angle direction X with respect to the drive rotating body 11 as the rotational torque increases in the direction X, the planetary rotating body 15 has the first planetary gear portion 154 and the first sun gear. The driven rotor 14 is advanced with respect to the drive rotor 11 by performing planetary motion while changing the meshing position with the portion 123 and the meshing position between the second planetary gear portion 155 and the second sun gear portion 143. Relative rotation in direction X The valve timing changes to the advance side, and the valve timing of the most advanced phase can be realized.

  Further, when the cylindrical shaft 16 rotates relative to the drive rotating body 11 in the retarding direction Y as the rotational torque increases in the direction Y, the motor 21 suddenly stops, etc., the planetary rotating body 15 is moved to the first planetary gear section. The driven rotator 14 is driven by a planetary motion while changing the meshing position of the first sun gear part 154 and the meshing position of the second planetary gear part 155 and the second sun gear part 143. 11 relative to the retarding direction Y. Therefore, when the valve timing changes to the retard side, and particularly when the motor 21 is suddenly stopped, the most retarded phase valve timing at which the internal combustion engine can be started can be realized.

Hereinafter, effects derived from the configuration of the present embodiment will be described.
(1) In this embodiment, the urging member 172 is formed of bimetal, and has a characteristic that the urging force toward the meshing side increases as the temperature increases, and the urging force decreases as the temperature decreases.

  Thereby, the urging member 172 urges the planetary rotator 15 toward the meshing side with a high urging force at a high temperature. For this reason, when the viscosity of the lubricating oil is reduced due to high temperature, the first planetary gear portion 154 and the second planetary gear portion 155, the first sun gear portion 123 and the second sun gear portion 143 are engaged with each other, and an abnormal noise is generated. Can be suppressed.

  On the other hand, the urging unit 17 is a planetary rotator to the meshing side of the first planetary gear unit 154 and the second planetary gear unit 155, the first sun gear unit 123 and the second sun gear unit 143 with a low urging force at low temperatures. Energize 15. Therefore, when the viscosity of the lubricating oil increases due to low temperature, the friction torque between the planetary rotor 15 and the drive rotor 11 and the driven rotor 14 can be reduced, and the planetary rotation driven and rotated by the motor 21 is reduced. The responsiveness of the body 15 can be improved.

  (2) In the present embodiment, the urging member 172 has a high expansion layer 173 and a low expansion layer 174 in the plate thickness direction, the high expansion layer 173 is formed inside, and the low expansion layer 174 is formed outside. ing. Thereby, the opening degree of the U-shaped biasing member 172 increases as the temperature increases, and the opening degree decreases as the temperature decreases. Therefore, the urging force of the urging member 172 toward the meshing side increases as the temperature increases and decreases as the temperature decreases.

  (3) In the present embodiment, a plurality of urging portions 17 are provided. Thereby, the stability of the urging force that urges the planetary rotator 15 toward the meshing side can be improved. Further, the plurality of urging portions 17 are provided on both sides in the circumferential direction of the thickest portion 164 where the portion is formed to be thickest in the radial direction. Thereby, the planetary rotator 15 can be urged with good balance toward the meshing side, and the effect of suppressing the generation of abnormal noise and improving the responsiveness can be further enhanced.

(Second Embodiment)
A valve timing adjusting device according to a second embodiment of the present invention is shown in FIGS. In the second embodiment, only the parts different from the first embodiment will be described, and the description of the same configuration as that of the first embodiment will be omitted. Moreover, the same code | symbol is attached | subjected about the component similar to 1st Embodiment.

In the present embodiment, as shown in FIG. 5, the urging portion 27 includes an accommodation recess 271, an urging member 272, and a seat surface portion 273.
The housing recess 171 is a recess that is recessed a predetermined distance radially inward from the outer wall of the eccentric portion 162, and a groove 277 is formed at the bottom.

  The urging member 272 is a metal leaf spring that is housed in the housing recess 171 and has a substantially U-shaped cross section perpendicular to the axial direction of the cylindrical shaft 16. In the present embodiment, the biasing member 272 is a leaf spring formed of, for example, iron.

  The seat surface portion 273 is formed in a plate shape and is provided in the groove portion 277. The seat surface portion 273 has a high expansion layer 274 and a low expansion layer 275 in the plate thickness direction. The high expansion layer 274 and the low expansion layer 275 are formed of two different types of metals. The high expansion layer 274 is, for example, an alloy containing nickel, iron, and chromium, and has a predetermined coefficient of thermal expansion. The low expansion layer 275 is, for example, an alloy containing nickel and iron, and has a thermal expansion coefficient lower than that of the high expansion layer 274. That is, the seating surface portion 273 is formed from bimetal. The high expansion layer 274 is formed on the radially outer side of the cylindrical shaft 16, and the low expansion layer 275 is formed on the radially inner side of the cylindrical shaft 16. The urging force of the seating surface portion 273 toward the meshing side increases as the temperature increases, and decreases as the temperature decreases.

In the present embodiment, the same effects as those of the first embodiment are exhibited.
The seat surface portion 273 is a bimetal plate having a two-layer structure in the plate thickness direction, and the coefficient of thermal expansion of the radially outer layer of the cylindrical shaft 16 is higher than the coefficient of thermal expansion of the radially inner layer of the cylindrical shaft 16. As a result, the plate-like urging member 273 is greatly deformed as the temperature increases, and is deformed as the temperature decreases. Therefore, the urging force of the urging member 273 toward the meshing side increases as the temperature increases, and decreases as the temperature decreases.

(Other embodiments)
In the above embodiment, an example in which the valve timing adjusting device adjusts the valve timing of the intake valve has been described. On the other hand, in another embodiment, the valve timing adjusting device may adjust the valve timing of the exhaust valve.

  In the above embodiment, an example has been described in which the driving rotating body rotates in conjunction with the crankshaft and the driven rotating body rotates in conjunction with the camshaft. On the other hand, in another embodiment, the driven rotator may rotate in conjunction with the crankshaft, and the drive rotator may rotate in conjunction with the camshaft.

  In the said embodiment, the example provided with two urging | biasing parts was shown. On the other hand, in another embodiment, it is good also as providing one or three or more urging | biasing parts.

  In the above embodiment, an example in which the high expansion layer is formed of an alloy containing nickel, iron, and chromium, and the low expansion layer is formed of an alloy containing nickel and iron is shown. On the other hand, in other embodiments, the high expansion layer and the low expansion layer may be made of an alloy containing another metal.

  In the said embodiment, the biasing member or the seat surface part showed the example formed from a bimetal. On the other hand, in other embodiment, it is good also as forming both a biasing member and a seat surface part with a bimetal.

  In the said embodiment, the example formed so that an urging | biasing member might be bent in U shape was shown. On the other hand, in other embodiments, the urging member may be formed to be bent in a V shape, an O shape, an S shape, a C shape, or the like.

  The present invention described above is not limited to the above-described embodiment, and can be applied to various embodiments without departing from the gist thereof.

1 ... engine (internal combustion engine),
4, 5 ... camshaft (driven shaft),
8 ... Intake valve,
9: exhaust valve,
2 ... Crankshaft (drive shaft),
10 ... Valve timing adjusting device,
11 ... Drive rotator (first rotator),
12 ... Drive gear member,
14 ... driven rotor (second rotor),
15 ... Planetary rotating body,
16 ... Cylinder shaft,
17, 27 ... Biasing part,
123 ... 1st sun gear part,
143 ... second sun gear part,
153 ... shaft hole,
154 ... 1st planetary gear section,
155 ... second planetary gear section,
175 ... Bottom (seat surface),
172, 272 ... biasing member,
273 ... Seating surface portion.

Claims (5)

An intake valve (8) and an exhaust valve (8) provided in a driving force transmission system for transmitting the driving force of the internal combustion engine (1) from the driving shaft (2) to the driven shafts (4, 5) and driven to open and close by the driven shaft. 9) A valve timing adjusting device (10) for adjusting the opening / closing timing of at least one of 9),
A first rotating body (11) that is formed in a cylindrical shape, has a first sun gear portion (123) on the inside, and rotates in conjunction with one of the drive shaft and the driven shaft;
A second rotating body that is formed in a cylindrical shape, has a second sun gear portion (143) having an inner diameter different from that of the first sun gear portion, and rotates in conjunction with the other of the drive shaft and the driven shaft ( 14)
It has a first planetary gear portion (154) meshing with the first sun gear portion, a second planetary gear portion (155) meshing with the second sun gear portion, and a shaft hole (153), and performs planetary motion. A planetary rotating body (15) for changing a relative rotational phase between the first rotating body and the second rotating body,
There is an urging portion (17, 27) for urging the planetary rotating body toward the meshing side of the first planetary gear portion, the second planetary gear portion, the first sun gear portion, and the second sun gear portion. And a cylindrical shaft (16) provided in the shaft hole so as to be rotatable relative to the planetary rotator, and rotatably supporting the planetary rotator,
The urging unit increases the urging force as the temperature increases, and decreases the urging force as the temperature decreases. The urging portion includes an urging member (172, 272) and a seat surface portion (175, 273) that contacts the opposite side of the urging member to the meshing side.
2. The valve timing adjustment device according to claim 1, wherein at least one of the biasing member and the seating surface portion is formed of a bimetal.   The urging member (172) is formed by bending a bimetal plate having a two-layer structure in the plate thickness direction into a U shape, and the thermal expansion coefficient of the inner layer is higher than the thermal expansion coefficient of the outer layer. The valve timing adjusting device according to claim 2.   The seating surface portion (273) is a bimetal plate having a two-layer structure in the plate thickness direction, and the thermal expansion coefficient of the radially outer layer of the cylindrical shaft is the thermal expansion coefficient of the radially inner layer of the cylindrical shaft. 4. The valve timing adjusting device according to claim 2, wherein the valve timing adjusting device is higher.   The valve timing adjusting device according to any one of claims 1 to 4, comprising a plurality of the urging portions.

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